BR0206152B1 - four vane rotor for use on a batch intensive internal mixing machine and batch internal mixing machine. - Google Patents

Description

"FOUR FLIP ROTOR FOR USE IN AN INTENSIVE PUNCHING INTERNAL MIXING MACHINE AND PUNCHING INTERNAL MIXING MACHINE".

Field of the invention

This invention relates to improved rotors for internal batch mixing machines having two non-engaging, counter-rotating four-wing rotors. The four fin rotors of this invention provide improved dispersive and distributive mixing of materials in the batch mixer. The invention also relates to batch mixing machines employing two of the novel invention four-wing rotors, and to improved batch mixing using two batch mixing machines having the improved four-wing rotors.

Background of the invention

This invention relates to high-intensity batch-type internal mixing machines having a shaped mixing chamber to accommodate two counter-rotating non-rotating fin rotors. The abatement of ingredients to be mixed into a homogeneous mass is fed down into the mixing chamber via a vertical chute and is pushed down under pressure by a piston located in the chute. Steppe is hydraulically or pneumatically driven. The lower piston face, when advanced down to its operating position during batch mixing, forms an upper portion of the mixing chamber. The homogeneous mixture produced is removed from the mixing chamber through a discharge opening at the bottom of the chamber, and a door associated with this opening is then closed to the next batch of ingredients to be introduced down through the chute.

Some internal batch mixing machines are designed with non-gear rotors, and others have gear rotors. Geared rotors should always be rotated at the same rotational speed in synchronized relationship; Non-geared rotors can be driven at the same rotational speed or at different rotational speeds to achieve different mixing and kneading effects. The present invention relates to the non-engaged type. The rotor fins have a generally helical configuration, and they produce high intensity mixing and homogenization through the cooperative interaction of their various potent dynamic effects, as described later. For further information on such internal batch mixers having unengaged rotors, reference may be made to US patents 1,200,070 and 3,610,585, assigned to predecessors of this recess, and recent US patents 4,744,668 and 4,384,543, and disclosures of these patents are incorporated herein by The vast majority of all batch internal mixing machines in commercial use today in the United States having non-geared rotors are operated non-synchronously, ie with rotors being driven at different rotational speeds, often called "ratio mode". deatrite ". For example, a non-synchronous operation causes one rotor to produce 9 revolutions versus 8 revolutions for the other rotor, ie a "friction ratio" of 9 to 8 or 1,125 to 1.

U.S. Patent No. 4,744,668, issued May 17, 1988, discloses new four-wing fin and improved performance four-wing rotors adapted for use on any of the currently numerous non-synchronous flap mixers or asynchronous batch mixers.

US Patent No. 4,834,543 discloses four-vane non-geared rotors to be driven at synchronous speed at a constant 180 ° phase angle, with each of the two rotors used in the batch mixing machine having two long vanes and two short vanes in each. one of the two rotors.

In both U.S. patents 4,744,668 and 4,834,543, it is recognized that optimal or preferred results are achieved by driving the specified rotors synchronously while oriented in a preferred phase angle relationship. The patent specifies that preferred phase angle relationship to be about 180 °.

The four-gear unengaged (tangential) rotors hitherto proposed for use with synchronous rotating internal batch mixing machines have been of the type that promotes primarily micro-dispersive (intensive) mixing due to the intensive shear forces generated by the rotor chamber. mixture. In dispersive mixing, the high-generated shear forces rapidly break up clumps in the batch of materials to be mixed. Unengaged rotors also have the properties of providing high fill factors and short feed and discharge times together with excellent dispersive mixing characteristics. However, such non-geared rotors do not provide essentially equally good (extensive) distributive mixing of the materials to be mixed. Also, the use of such unengaged rotors may be characterized by an undesirable rise in material temperature to be mixed.

On the other hand, mixing machines hitherto employing geared motors have better thermal transfer characteristics and better thermal control over blended mixing. Also, in contrast to mixing machines employing non-geared rotors, machines employing geared rotors exert high elongation deformations in the wedge region between the two rotors producing good current division and thus good distributive mixing. In contrast, a mixing machine employing non-geared rotors only smooth division of current is produced in the region and therefore generally does not produce essentially equivalent distributive mixing. There is therefore a need for rotors for use in debated mixers that simultaneously produce good dispersive mixing and good distributive mixing in the dated processing of materials to be mixed and thereby reap the benefits of both non-meshed and rotor-driven rotors.

Summary of the invention

The invention provides a novel four-vane rotor design in which each rotor vane performs a specific function, and the use of these rotors as synchronously driven rotors in mixing machines to produce both good and distributive dispersive mixing in good mixing and good process temperature control, and thereby to provide better utilization of the blender chamber and to produce a more thermally and compositionally homogeneous blended product. In the rotors of this invention certain fins provide primarily dispersive mixing and certain fins provide primarily distributive mixing in the batch.

A further aspect of this invention is that the use of new rotors in mixing machines forces certain flow patterns in the window of interaction between the two blender rotors and produces more efficient exchange of material between one rotor chamber and the other blender rotor chamber. This function is performed in part by a rotor fin having a substantial helical extension such that a rotor fin is present in the window of interaction between the two rotors at almost all times. This allows for great flexibility in affecting flow patterns in the window of interaction between the two rotors. Another aspect of this invention is the ability to essentially eliminate any stagnation area possible within the mixing chamber by the fin design of this invention and proper alignment of the rotors in the mixing chamber. mixture. A still further aspect of this invention is the ability to vary blending intensities during the mixing cycle due to the geometry of the new finned rotors of this invention along with the rotor speeds employed.

The four-vane rotor of this invention for non-engaging synchronous rotation with an identical four-vane non-engaging rotor in a batch intensive mixing machine having synchronous drive means comprises a rotor having a geometrical axis and an axial extension from a first end of the rotor to a second opposite end of the rotor having four generally helical configuration fins including first and second long fins and first and second short fins. The first long fin seorigins at the first end of the rotor in a rectangular position at about 0Â ° to the dorotor geometry axis and has a rotor-oriented eixogeometric fin tip at a propeller angle between about 45Â ° and 60Â ° and has a axial length between about 60% about 80% of the rotor axial length. The first long fin has an angle of attack of about 25 ° to 60 °. The second long rotor fin originates at the second end of the rotor at an angular position of about 220 ° to about 240 ° with respect to the rotor geometry axis and has a rotor-oriented shaft end at a propeller angle between about 20 ° C. ° to 40 ° and has an axial length between about 60% to 80% of the rotor axial length; The second long fin has an angle of attack of about 15 ° to 25 °. The fin tips of each of the first and second long fins have a width, if measured normal to the fin helix angle, with the width of the first long fin tip being at least 50% and up to. 100% wider than the width of the second long flute tip. The first short fin on the rotor seizes at the first end of the rotor in a rectangular position in the range of about 170 ° to about 180 ° with respect to the rotor geometry, and has its flap tip oriented towards the rotor geometry at a propeller angle. in the range of about 25 ° to 60 °, preferably substantially equal to the helix angle of the vane tip of the first long rotor, and has a second axial length between about 10% and 30% of the rotor axial length. The second norotor short vane originates at the second end of the rotor in an angular position in the range of about 350 ° to about 20 ° with respect to the rotor geometry, with its tip facing the rotor geometry in a propeller angle in the range of about 25 ° to 60 °, preferably substantially equal to the helix angle of the second long rotor vane tip, and has an axial length of between about 10% and 30% of the rotor axial length. Each of the first and second short fins of the first and second short fins has their fin points a radial distance essentially equivalent to the radial distance of the rotor geometry axis.

When two of these rotors are placed in a synchronously operated batch mixer, the rotors are oriented in the mixer mixing chamber such that the first rotor long fin helical tip guide is located on a first rotor collar that is at an opposite end of the mixer. second rotor collar mixing chamber where the guide edge of the helical fin tip of the first long rotor fin is located.

Additionally, the two rotors are positioned in the mixing chamber such that during their non-engaging counter-rotation the leading edge of the first long second fin rotor flap follows the first fin helical flap extending first rotor rotating through the deinteraction window between the two rotors from 90 ° to 180 °, preferably about 90 °. In this 90 ° fence orientation, and as a result of the twisting angles of the two rotor vanes, each rotor fin provides effective cleaning of the adjacent rotor processing surfaces thus providing effective material renewal on these surfaces. The large and small fins on the two rotors essentially completely clean the entire mixer region in the space between the two rotors thus ensuring additional intensification of distributive mixing.

Other angular positions of previously rotationally aligned alignments other than 90 ° and up to 180 ° may be employed to promote other aspects of the mixing process, such as for example collecting and discharging material from the mixer. At such enlarged angular positions of the origin points of the leading edges of the first fin coils on the two rotors, a wider open space between the two rotors is provided at an angular position followed by a complete sweep of the region by the other rotor fins when the last cross is crossed. the interaction window of the two rotors.

Brief Description of the Drawings

The invention is illustrated by but limited to the invention as shown in the accompanying drawings in which:

Fig. 1 is an elevational view of an internal batch mixing machine for employing the rotors of this invention, with portions of the mixing machine in section;

Fig. 2 is an enlarged sectional plan view taken along line 2-2 in FIG. 1 through the blending chamber;

Fig. 3 is a diagrammatic illustration showing the meaning of rotor profile terminology used in this patent application;

Fig. 4 is a plan view of the four vane rotors of this invention as oriented in the blending machine without showing the mixing machine;

Fig. 4A is a side elevational view of the dafig rotors. 4 looking in the direction of arrow A in fig. 4;

Fig. 4B is a side elevational view of the dafig rotors. 4 looking in the direction of arrow B in fig. 4; and

Fig. 5 is a schematic view of a rotor developed of this invention for the purpose of illustrating and explaining the rotors of this invention and where in their developed form the rotor helical fins appear straight and diagonally oriented lines representing the decent lines of the fin tips.

Detailed Description of the Invention

As shown in fig. 1, a batch-type high intensity in-house mixing machine, generally indicated at 20, in which a pair of non-engaged rotors 21 and 22 configuring the present invention may be used to assist include a vertically interchangeable piston 24 movable between an elevated position shown in FIG. 1 and a lowered operating position 24 'shown in dashed outline. This piston 24 is used to move ingredients to be mixed down into a mixing chamber 26. In this operating position 24 ', it opposes the forces exerted by materials in the mixing chamber 26 as they are being completely and intensely mixed by the fins at later described in the two counter-rotating rotors 21 and 22, which are rotated about spaced parallel horizontal geometric axes, as shown by arrows 23 and 25. The left rotor 21 as seen in FIG. 1 is rotated in a clockwise direction about its geometric axis and rotor 22 in a counterclockwise direction. The blending chamber 26 is shaped to accommodate these two rotors and includes left and right chamber cavities 27 and 28 each of a generally circular cylindrical shape. These chamber cavities are positioned in horizontally opposite relationship open against each other. There is a central region 29 of the mixing chamber 26 which is defined as being generally located between the two rotors 21 and 22. The ingredients to be mixed are initially introduced into a hopper 30, while the piston 24 is raised such that the ingredients may enter a chute. 32 communicating with the hopper 30 and guided downwards into the center region 2 of the blending chamber 26. Then the piston is lowered to push the ingredients down into the mixing chamber and retain them there. This piston is shown to be operated by a fluid actuated drive cylinder 34 mounted on top of the overall housing 35 of the mixing machine 20.

The hydraulic or pneumatic fluid cylinder 34 contains a double acting piston 36 with a piston rod 38 connected to piston 24 to lower and raise the piston. The piston is clamped to the lower end of the piston rod 38 below the lower end 39 of cylinder 34. Actuating fluid under the desired pressure is fed through a supply line 40 into the upper portion of cylinder 34 to force piston 36 down into position. operating position 24 '. After the mixing operation is completed, the piston is retracted back to its raised position by actuating fluid fed into the cylinder 34 below the piston 36 by a supply line not seen in FIG. 1.

The mixed and homogenized materials are discharged from the bottom of the mixing chamber 26 through a discharge opening normally closed by a door 42 which is held in its closed position during the mixing operation by a locking mechanism 44. The door 42 when released by the locking mechanism locking44 is hinged downwards on a hinge axis 46. The door is hinged, for example, by a pair of hydraulic torque motors, not shown, mounted at opposite ends of the hinge axis 46. FIG. 2 is a plan sectional view of the blending mechanism 20 of FIG. 1 outlet along line 2-2. Rotors 21 and 22 are rotated in opposite directions 23, 25 by a gear mechanism 48 which is driven by a drive motor 50. This gear mechanism 48 comprises identical geared gears to drive the rotors at the same time, nominally, synchronous speeds. The drive motor 50 may be conventionally configured and preferably includes speed control means for varying the rotor rotational speed for the rotors as desired depending upon the particular ingredients in the blending chamber 26 and their temperature and viscous state, depending on the desired rate. of mixing power to be supplied by the rotors.

There are conventional sealing collars 54 (fig. 2) located immediately adjacent each end of each rotor to seal the mixing chamber 26. The ends of the rotors adjacent the respective collars 54 are called the "collet end". 2, the left and right rotors 21 and 22 are each shown having an axial rotor length "L" measured between their respective collar ends 57 and 58. The collar end 57 connected to drive shaft 55 or 56 is the "driven end" of the rotor, the other collar end 58 being the "cooling end" or "water end". The rotors contain cooling passages, and refrigerant, which is usually water, is fed into these passages at opposite ends of the location of drive shafts 55 and 56. Each of the rotor envelopes, defined by the tip diameter, has a diameter "D" as shown in fig. 3. Therefore, the developed length of each rotor envelope is, "ττ D", as shown in fig. 5. Fig. 3 illustrates the terminology used in connection with the description of the rotors of this invention. Referring to FIGS. 4, 4A and 5, a rotor configuration of this invention is illustrated. The rotor has two long fins 35, 61 and 62 originating from the post-collar ends. The term "originating from" or similar language means that the guide edge of the respective fin loop 61 or 62 is located at the designated take-off end. The rotor geometry is indicated at 60, and the angular positions 0 degree, 90 degrees, 180 degrees, 270 degrees, and 360 degrees of the developed rotor envelope are angular positions on the rotor eixogeometric. The angular position of 0 degrees or 360 degrees is defined for convenience of explanation with reference to Figs. 4, 4A 4b and 5, as being that position in the rotor envelope adjacent to the central region29 and being in a horizontal plane containing the rotor geometrical axes 60. This plane is also referred to hereinafter as the interaction window between the two rotors. Similarly, the rotor also has its two short fins 63 and 64 originating from opposite collar ends.

An envelope developed from a rotor illustrative layout of the invention is shown in fig. 5. In this figure the rotor vanes are represented by a decent line of the respective vane tips, with the width of the vane tips being shown separately. In rotor 21 the first long fin 61 originates at an axial end of the rotor at about the 0 ° angular position with respect to the rotor geometry and has a 50 ° helix angle. The axial length Li of this first long fin is 73.3% of the rotor axial length L. Flap tip width of this flip is Wi. The width of the fin is measured normal or perpendicular to the helix angle of the fin. The second long fin 62 originates from the opposite axial end of the rotor about 230 ° from the geometrical axis of the rotor and has a helix angle of 33 °. The axial length L2 of this second long fin is 73.3% of the axial length L of the rotor. The tip width of this fin is W2. Width W1 is 55% greater than width W2. The first fin 63 originates at the same axial end of the rotor as the first long fin 61, but in a rectangular position with respect to the rotor geometry of 180 ° and has a helix angle of 50 °. The axial length L3 of this first short fin is 20% of the axial length L of the rotor. The width of the fin tip of this fin is W3. The second short fin 64 originates at the same axial end of the rotor as the second long fin 62 but has an angular position with respect to the 5 ° rotor geometry and has a helix angle of 33 °. The wide tip of this fin is W4. W3 width is 55% larger than W4 width.

Figs. 4, 4A and 4B illustrate the relative orientation of the fins when two of the rotors are employed in an intensive batch internal mixing machine as described in FIG. 1. One means for controlling extensive mixing in such batch mixers is by orienting the rotor vanes with respect to each other such that the rotor vanes of each rotor cross the interaction window between the rotors in a predetermined configuration to force material exchange. from one mixer chamber to the other mixer chamber. The first long fin 61 of each rotor 21 and 22 with the relatively large propeller angle and distortion or axial length Li provides the sweep of the interaction window between the two rotors. These flow patterns are further enhanced by the second long fins 62 and the two short fins 63 and 64 which are designed such that a rotor vane is always present in the interaction window between the two rotors for the entire duration of each rotor rotation. A preferred rotor orientation has the origin point 71 of the first long fin 61 of the first rotor 21 entering the window of interaction between the rotors within an angular orientation in the range of 0 ° to 25 ° from the entry point 72 of the second long fin 62 of the second rotor. 22 within the interaction window. In this arrangement, and as a result of the propeller angles of the two rotor vanes, each rotor van provides an effective scan of the adjacent engine processing surfaces providing effective material renewal on these surfaces. The long and short rotor vanes of the two rotors essentially completely sweep the entire mixer region in the space between the two rotors thus ensuring further intensification of extensive mixing. It is further desired that the origin point input 71 of the first long fin of a rotor21 within the interaction window follows the origin point input 73 of the first long fin 61 of the second rotor 22 by an angular position of 90 ° to 180 °.

However, it will be appreciated that other rotor alignments are possible which will promote other aspects of the mixing process such as inlet and discharge of mixer material.

In the rotors of this invention, the helix angle of the first long fin 61 is chosen to balance the amount of material that is allowed to pass over rotor vane tip thrust and along the rotor vane length L in the axial direction. A 45 ° to 60 ° propeller angle for this first long fin ensures that an excess of 50% of the material accumulated in front of the rotor vane 61 is forced to axial direction for extensive mixing and temperature control of intensified material. The bulk of material accumulated in front of the rotor vane 61 progressively flows circumferentially over the rotor vane tip. With this the correct selection of the rotor propeller angle ensures the correct radial and axial material flow proportions, the rotor vane twisting length or its equivalent axial length of 60 to 80% of the rotor length controls the extent of axial material flow.

Therefore, the rotors of this invention ensure that a significant proportion of the material accumulated in the front of the first long rotor fin 61 will pass through most of the mixing chamber.

Placement of the second long fin 62 of the rotor and angled placement of 220 ° to 240 ° with respect to the rotor shaft allows material to be freely transferred from one rotor fin to another. The 20 ° to 40 ° propeller angle for this flap 62 ensures that a substantial amount of material flows into the rotor radial clearance between the rotor vane tip and the inner wall of the mixing chamber housing.

Dispersive mixing is achieved by repeatedly subjecting the material to controlled stress during finite times. Among the design parameters that affect the stress level imposed on the material as it flows through the radial clearance between the rotor vane and the inboard wall housing are the shear rates. predominant material viscosity. The latter is characteristic of the molecular structure of the material being processed and the processing temperature. The rotors of this invention provide effective means by which this temperature can be effectively controlled. Thus, the detention levels are dependent on the shear rate and temperature. The amount of material allowed to flow into the radial clearance between the rotor vane tip and the chamber wall surface is a function of the counter clearance and the angle of attack on the rotor vane working surface. In this invention the rotor design parameters allow effective control over the amount of material passing through this section of the mixer.

Another means employed in the rotors of this invention for controlling the mixing intensity is by selecting the width of the rotor vane tip according to the desired processing activity for each vane. Accordingly, equal fin tip width can be used for both long fins and / or both short fins, it is preferred that the fin width of the first long fin 61 is at least 50% larger, and even about 100% larger than the width. Similarly, it is preferred that the width of the first short fin 63 is at least 50% greater than the width of the second short fin 64. It has also been found desirable that the width of the first short fin 63 be equal. the width of the first fin 61 and that the width of the second short fin 64 is equal to the width of the second long fin 62.Larger fin widths increase the intensity of the mix as the mixing duration as a result of shear material increases with the edge widths of rotor fin increasing. If desired, linear variations in rotor fin width from the origin of the rotor fin to the termination point of the rotor fin can be used to further optimize the characteristics of each rotor fin mix.

The short rotor fins 63 and 64 of this invention act to divert material away from the rotor fin origin points and thus away from the extreme plates of the mixing chamber. These fins divert material away from the end plates and eliminate possible areas of relatively poor material flow stagnation, i.e. reduce the amount of material allowed to enter the region at the two rotor ends and thereby reducing the wear experienced in these regions. The point of origin of the angular fins and the axial length of the fins is chosen to achieve the purposes while allowing uninterrupted free flow of material of long circumferential and axial bending length.

Another aspect of the rotors of this invention is the different angles of attack for the rotor vanes. The angle of attack is the angle formed by the tangents with the inner face of the chamber and the working surface of the motor in the vicinity of the rotor vane tip. A "wedge" region is formed in the vicinity of the rotor tip and a suitable flow of material over the tip of the rotor. For the first long rotor 61, the angle of attack ranges from 25 ° to 60 ° and primarily promotes flow of axial rather than circumferential material. The second angle of attack of the long fin 62 ranges from 15 ° to 25 ° and ensures that most of the material trapped in the rotor fin wedge region will be forced onto the rotor fin through the radial clearance formed by the rotor fin tip and the inner wall of the rotor fin. chamber. In a preferred embodiment of this invention the first short flap angle 63 is at least 5 °, preferably 5 ° to 15 °, greater than the second short flap angle of attack 64. Therefore, the first short flap primarily promotes distributive mixing and the second short flap primarily promotes dispersive mixture.

In another aspect of the rotors of this invention, the leading angles of the two long vanes 61 and 62 may also be varied along the length of the long rotor vanes to influence the amount of material allowed to flow axially or circumferentially over each fin tip. For example, the angle of attack for the first long rotor fin 61 could range from a minimum of 60 ° at the rotor fin origin point to 25 ° at the rotor fin determination point, and for the second fin 62 of an angle of attack from 25 ° at its point of origin to an angle of attack of 15 ° at its point of determination. Generally, the angle of attack of the first long fin 61 will be at least 5 °, preferably 5 ° to 15 °, greater than the angle of attack of the second fin 62. The correct selection of appropriate attack angles allows an additional means to balance between mixing characteristics. and distributive distribution of each of these rotor vanes and the system employing them.

The rotors of this invention produce increased productivity on intensive, in-house mixing machines by employing them. In addition, they also produce products of greater uniformity and homogeneity in a shorter period of time. Productivity increases of generally at least 20% or more can be achieved with non-invention rotors compared with prior art rotor results. The rotors allow for reduced cycle time for batch mixers, and also allow for a significant reduction in the discharge temperature of processed material.

It will be appreciated that the invention has been illustrated by certain embodiments thereof and that modification and alterations thereof may be made without departing from the spirit and scope of the disclosed invention.

Claims (19)

1. Four-wing rotor for use in a batch-intensive internal mixing machine, characterized in that the rotor has a geometrical axis (60) and an axial length from a first rotor end to a second opposite rotor end and multiple flaps ( 61, 62, 63, 64) of generally helical configuration including first and second long fins (61, 62) and first and second short fins (63, 64); the first long fin originating at the first rotor end at an angular position of about 0 °. with respect to the rotor geometry axis and having a rotor tip axis oriented shaft in a propeller angle between about 45 ° and 60 ° and having an axial length between about 60% to about 80% of the rotor axial length and a angle of attack at the band about 25 ° to 60 °, the second long fin on the rotor originating at the second end of the rotor at an angular position of about 220 ° to about 240 ° in re with respect to the rotor geometry axis and having a rotor eixogeometric oriented fin tip at a propeller angle between about 20 ° to 40 ° and having an axial length between about 60% to 80% of the rotor axial length and a angle of attack between about 15 ° and 25 ° with the provision that the angle of attack of the first long fin is greater than the angle of attack of the second long fin by at least 5 °, the fin tips of each of the first and second long fins having a width, as normal measure to the vane helix angle, with the width of the first long vane tip being at least 50% wider than the width of the second long vane tip, the first short rotor vane originating at the first end of the rotor at a angular position in the range of about 170 ° to about 190 ° with respect to the rotor axle, having a fin tip oriented toward the rotor geometry at a propeller angle in the range of about and 25 ° to 60 °, and having an axial length between about 10% and 30% of the rotor axial length, the second short fin on the rotor originating at the second end of the rotor at an angular position in the range of about 350 ° to about 20 ° to the rotor axis, having a vane tip oriented toward the rotor geometry at a propeller angle in the range of about 25 ° to 60 °, and having an axial length between about 10% and 30% of the length. rotor axial; Each of the first and second long fins and the first and second short fins having their flange ends an essentially equivalent radial distance from the rotor shaft. Four-wing rotor according to Claim 1, characterized in that the angle of attack of the first long fin is greater than the angle of attack of the second long fin of from about 5 ° to about 25 °. Four-wing rotor according to Claim 1, characterized in that the angle of attack of the first short fin is between about 25 ° and 40 °, the angle of attack of the second short fin is between about 15 ° and 25 °. , provided that the angle of attack of the first short fin is greater than the angle of attack of the second short fin by at least 5 °. Four-wing rotor according to Claim 3, characterized in that the angle of attack of the first short fin is between about 25 ° and 40 °, the angle of attack of the second short fin is between about 15 ° and 25 °. , provided that the angle of attack of the first short fin is greater than the angle of attack of the second short fin by at least 5 ° to about 15 °. Four-wing rotor according to Claim 4, characterized in that the angle of attack of the first short vane is essentially the same as the angle of attack of the first long vane and the angle of attack of the second short vane is essentially the same as the angle of attack. second long fin attack. Four-wing rotor according to Claim 5, characterized in that the leading angles of the first long fin and the first short fin are about 29 ° and the angles of the second long fin and the second short fin are each about 19 °. Four-wing rotor according to Claim 1, characterized in that the propeller angles of the first long fin and the first short fin are about 50 ° and the propeller angles of the second long fin and the second short fin are each about 33 °. Four-wing rotor according to Claim 6, characterized in that the propeller angles of the first long fin and the first short fin are about 50 ° and the propeller angles of the second long fin and the second short fin are each about 33 °. Four-vane rotor according to Claim 1, characterized in that each of the first and second short vane tips have a width, the width of the first vane tip being at least 50% wider than the width. from the second short fin tip. Four-fin rotor according to claim 9, characterized in that the width of the first long fin tip is about 64% wider than the width of the second long fin tip, the width of the first short fin tip is 64. % wider than the width of the second short fin tip, with the width of the first short fin tip being essentially equal to the width of the first long fin tip and the width of the second short fin tip being essentially equal to the width of the second long fin tip. Four-wing rotor according to Claim 8, characterized in that each of the first and second short vane flap ends have a width as a normal measurement of the vane helix angle, with the width of the first short vane being at least 50% wider than the width of the second aletacurta tip. Four-fin rotor according to claim 11, characterized in that the width of the first long fin tip is about 64% wider than the width of the second long fin tip, the width of the first short fin tip being about 64% wider than the width of the second short fin tip, with the width of the first short fin tip essentially being the width of the first long fin tip and the width of the second short tip essentially equal to the width of the second long fin tip. Four-wing rotor according to Claim 1, characterized in that the second long fin is in an angular position of about 230 °, the first short fin originates in an angular position of about 180 °, and the second short fin. originate at an angular position about 5 ° to the rotor geometry. Four-wing rotor according to Claim 8, characterized in that the second long fin originates in an angular position of about 230 °, the first short fin originates in an angular position of about 180 °, and the second fin. originate in a rectangular position of about 5 ° with respect to the dorotor geometric axis. Four-wing rotor according to Claim 10, characterized in that the second long fin originates at an angular position of about 230 °, the first short fin originates at an angular position of about 180 °, and the second short fin. give rise to angular deposition of about 5 ° with respect to the rotor eixogeometric. Four-wing rotor according to claim 12, characterized in that the second long fin originates at an angular position of about 230 °, the first short fin originates at an angular position of about 180 °, and the second fin short angle originate an angular deposition of about 5 ° to the rotor eixogeometric. 17. Internal batch mixing machine, including a housing defining a mixing chamber with respective cavities accommodating first and second counter-rotating fin motors, not engaged in parallel geometric shafts in said cavities, ascending cavities communicating in a central region of the generally located mixing chamber between said rotors to provide a window of interaction between said rotors, where each rotor has a driven end and an opposite cooling end with the driven end of each rotor being adjacent to each other in the cavities, each of the two rotors comprising a rotor as defined in either claim 1 to 6, characterized in that the rotors are oriented in the respective cavities such that the first long fin of the first rotor seorigines at the driven end of the first rotor and the first long fin of the second rotor originates from the cooling end of the s Second rotor. Mixing machine according to claim 17, characterized in that the rotors are oriented in the mixing machine such that the point of origin entry of the first long fin of a rotor in the window of interaction between the rotors runs through the point of origin. the first long fin of the other rotor by an angle of 90 ° to 180 °. Mixing machine according to Claim 17, characterized in that the rotors are oriented in the mixing machine such that the point of origin of the first long fin of the first rotor in the window of interaction between the rotors is within an angular orientation in the 0 ° to 25 ° range from the source point input of the second long fin (62) input of the second rotor (22) in the interaction window.